Calculating machine



Jan. 16, 1945. L p CROSMAN CALCULATING MACHINE Filed Aug. 21, 1943 5Sheets-Sheet l -aub mi w INVENTOR A TTORNE Y Jan. 16, 1945. R CROSMAN2,367,386

CALCULATING MACHINE Filed Aug. 21, 1945 3 Sheets-Sheet 2 gZh \f pATTORINEY Jan. 16, 1945. P. CROSMAN 2,367,386

CALGULAT ING MACHINE Filed Aug. 21, 1945 3 Sheets-Sheet 3 W 33 29 P Q 55Patented Jan. 16, 1945 UNITED STATES PATENT OFFICE CALCULATING MACHINELorlng Pickering Crosman, South Orange, N. 1., assignor to MonroeCalculating Machine Company, Orange, N. 1., a corporation of DelawareApplication August 21, 1943, Serial No. 499,742

9 Claims. (Cl. 102-145) The invention has relation to calculatingmachines, and more particularly to means for completing an operation andfor bringing the machine to rest with the parts in normal-position.

In rotary type calculating machines the operations of multiplication anddivision commonly involve repeated cycling of the differentialactuators, followed by a cycle terminating action responsive to a signalwhich may be transmitted at any stage of the operation, up to thefullcycle position of the actuators. U. S.Pate nt No. 1,566,650, issuedto George C.- Chase on December 22, 1925, shows means for bringing themachine to rest without shock by permitting a retarded overrun of thedifferential actuators beyond their full-cycle position in response to astopping signal, followed by the location of the parts in their normal,full-cycle positions.

. The completion of a machine operation, however, and the normalizing ofthe various control devices, may involve considerable drag upon theoverrun means, as for instance in completing the tens transfer action inthe register, as shown in U. S. Patent No. 1,845,863, issued to GeorgeC. Chase on February 16, 1932. It is an object of the present inventionto insure completion of the machine operation in a uniform manner underall conditions, by providing a positive drive of the differentialactuators beyond and reversely back to their full-cycle position.

The invention consists in the novel construction and combination ofparts, as set forth in the appended claims.

In the accompanying drawings, illustrating the invention:

Fig. 1 is a left side elevation of the clutch control mechanism of acalculating machine embodying the invention.

2 is a similar view of the main clutch and controlling elements.

Fig. 3 is a left side elevation of the rear portion of the calculatingmachine with the casingremoved, showing portions of the novel mechanism.

Fig. 4 is a front elevation of the clutches and driving connections.

Figs. 5, 6 and '7 are detail views of the locating cams, the harmonicstopping cams, and the auxiliary clutch respectively, shown in theirnormal positions of rest.

Figs. 8, 9 and 10 are corresponding views with the parts shown inpositions taken" during the cycling of the machine.

Figs. 11, 12 and 13 are corresponding views showing the parts in thepositions taken at the extreme limit of the overrun of the differentialactuators.

Transmission control means I05 (Figs. 2 and 4) through which power istaken from the electric motor I00 to operate the differential actuatorsof the calculating machine is herein termed the main clutch since itincludes two members engageable to effect the transmission. Thetransmission means is of the differential gear type disclosed in PatentNo. 1,566,650, hereinbefore referred to, this patent showing details ofsuch mechanism not herein specifically shown. With the motor runningidle two legs of the differential are driven in opposite directions.Upon interruption of rotation of one leg of the differential, byengagement of one arm of a clutch lever III with a lug I0I fixed uponthe rotating part, the third leg of the differential (having drivingconnection with the differential actuators of the calculator) will bedriven in a given (additive) direction, whereas interruption of rotationof the other leg of the differential, by engagement of the other end ofclutch lever III with a lug H0, fast to the rotating part, will effectreverse or subtractive rotation of the actuator.

The driven element of clutch I05 has gearing connection It with a shaftI0 having one-to-one driving connection with the differential actuators(not shown), shaft I9 also being provided with a crank arm 20, throughwhich the actuators are located in full cycle position at termination ofa calculating operation.

The selection of the arm of clutch lever III which is to be engaged withthe differential gear clutch I00 is effected by movement of a rock shaftI25 (Fig. 1), which may be rocked in one direction or the other by meansof add and subtract keys (as in Patent No. 1,566,650) or by means ofother operation control mechanisms. Shaft I25 is provided with an armhaving link connection H2 with a bell crank lever H3, said bell crankhaving ,pin and slot connection with a plate Ill (Fig. 2) slidablysupported upon a shaft H5, and having shoulder portions H6, H1 lyingabove and adjacent to pins fixed in the opposite arms of clutch leverIII, and upon rotation of shaft I25 in a counter clockwise direction asviewed in Fig. 1, plate III will be moved to the right as seen in Fig.2, and shoulder H6 will be brought into position over the left hand pinof clutch lever III. In this position of the parts depression of plate IIt will move clutch lever I I I into position to be engaged by one ofthe lugs I0'I of the clutch, and additive rotation of the diflerentialactuators will be eflected. Clockwise rotation of shaft I25, on theother hand, will move plate H4 to the left, and lug HI will lie abovethe opposite pin of clutch lever l l i, so that depression of plate H4will effect engagement of the clutch lever with a lug H of the clutch toeffect subtraction.

According to the present invention the main clutch is engaged by meansof an auxiliary clutch, this auxiliary clutch being also given a secondoperation to effect the stopping and rotation of the differentialactuators. The auxiliary clutch is tripped upon rocking movement ofshaft I25 in either direction, this engagement being effected by meansof a link 2i (Fig. 1) connecting bell crank lever I I3 with an arm 22,fast upon a shaft 23, shaft 23 being also provided with an arm 24 (Fig.3) having a roller normally lying between two lpawls 25, 25, mountedupon an intermediately fulcrumed lever 26. The lower arm of lever 26 hasa, lug 21 normally resting against a shaft 26 anad underlying a camportion of one element 29 of a toggle link. Element 29 is pivoted uponthe framing of the machine at 36, the associated element 32 of thetoggle having pivotal connection with a bail 33 (Figs. 1, 3 and 7)mounted upon shaft 28. Toggle 29, 32 normally locks ball 33 againstclockwise rotation under the influence of a spring 43, secured to an arm42 to be described. The detent 35 of the auxiliary clutch is alsomounted upon shaft 26 and has an arm lying in front of the ball 33, asseen in Fig. 7.

Upon rocking movement of the shafts I25 and 23 in either direction theroller of arm 24 will be brought against one of the pawls 25 and lever25 will be rocked counterclockwise as seen in Fig. 3, breaking toggle29, 32, and allowing the bail 33 to move the detent 35 out ofrestraining engagement with a pawl 36, pivoted upon the driven member ofthe clutch.

As shown, there are two clutch pawls 35, 31

' biased by a spring 39 for engagement with internal ratchet teeth ofthe driving element 39 of the clutch, these pawls engaging in oppositedirections, so that the driven element may not outrun the driver. Thepawls are provided with engaging extensions, pawl 36, when held out ofengaging position by detent 35, holding pawl 31 out of engagement. Thedriving member 39 of the clutch is fixed upon a shaft 40 (Fig. 4) havinggearing connection 4! with the shaft iii of motor Hill, which extendsthrough clutch Hi5.

In order to hold the sign determining slide H4 as set until the mainclutch may be operated, no matter how quickly the finger of the operatormay be removed from the operating key, a quick stroke latch is provided,comprising an arm 42 (Fig. 1) held by the spring 43 in contact with theball 33. Upon clockwise movement of ball 33 arm 42, which is pivotedupon the shaft 29, will follow in a clockwise direction, the free end ofthis arm engaging either above or below a lug 44, formed upon anextension of the arm 22 of shaft 23, according to the direction in whichsaid shaft has been rocked. l'hus arm 42 prevents the return of membms22, 2|, H3 and H4 to their normal unset position.

The auxiliary clutch having been engaged, the first action will be theunlocking of the difler- .rtial actuators from tne restraint of thedevices which normally h; '1 them in full cycle position. This locatingmeans comprises a pair of cams 45 (Figs. 3 and fixed for rotation withthe driven element of the auxiliary clutch. Normally cams 45 stand inthe position illustrated in Fig. 5, in which position both cams engagethe roller mounted in a rocker frame 43, having link connection with thecrank arm 23 of shaft I 3. Game being rotated in clockwise direction bythe auxiliary clutch, will move into the position illustrated in Figure8, wher n h y will lie out of the path of movement of the rollers ofrocker frame 46, leaving the differential actuators free to rotate.

Operation of the auxiliary clutch will effect engagement of the mainclutch as follows: Fast with the driven element of the auxiliary clutchis a notched disk 41 (Figure 1) having its periphery engaged by a rollermounted upon the end of an arm 45 fixed upon the shaft H5. An arm 49(Fig. 2) is also fixed upon shaft H5, this arm having pin and slotengagement with the free end of plate H4. Rotation of disk 41 by theauxiliary clutch will bring the notched portion thereof opposite theroller of arm 46, whereupon a spring 50 will rock the arms 49 and 49counterclockwise, bringing the lug H6 or the lug H! of plate H4 intocontact with the related pin of clutch lever iii, and rocking said leverto engage the main clutch.

Operation of the auxiliary clutch is now interrupted by engagement ofclutch pawl 38 with the inclined wall of a plate 5| (Figure 10) fixedupon the machine frame. Plate 5| is provided with an extended or dwellportion to prevent reengagement of the auxiliary clutch by the momentumof the disengaged driven elements.

During the calculating operation of the machine the auxiliary clutchdetent 35 will be re leased from restraint by bail 33, and the quickstroke latch 42 will be disengaged, as follows: Toggle element 29 isprovided with a cam extension 52 (Figure 3 which, in the broken oroperated position of the toggle will lie in the path of movement of aroller 53 mounted on a rocker frame 54 (Figure 6) having link connectionwith crank arm '20 of shaft i9, and in the rotation of said shaft roller53 will be rocked into en gagement with the cam portion 52 of toggleelement 29, moving bail 33 and arm 26 back to their normal positions,and reinstating toggle lock 29, 32.

At the end of a calculating operation the auxiliary clutch is reengagedby means of a lever 54 (Figs. 1, 10 and 13) fulcrumed upon the framingof the machine and normally latched in inoperative position by means ofan escapement device comprising primary and secondary latches 55, 56.Primary latch 55 normally engages a lug 51 of lever 54, said latch beingpivoted upon the framing at 58, and held in latching position by aspring 59. The ball 33 engages latch 55, and upon clockwise movement ofsaid bail, the latch will be disengaged from ing 57, whereupon lever 54will be moved slightly clockwise, by the action of a spring 66, intoengagement with the secondary latch 56, in which position lug 51 willlie above latch 55 and prevent the reengagement thereof. The signal fordisengaging the main clutch and bringing the actuators to rest may comethrough the manual release of the operation key, or through movement ofthe numeral wheels of thu. register, as set forth in Patent No.1,566,650. Ir case of manual release of the key a centralizing ornormalizing device 6| for the shafts I25 and 23 will operate to bringthe cam tooth 62 (Figure 1' into contact with a pin fixed in thesecondary latch 56, moving said latch out of engagement with lug 51 andallowing lever 54 to be fully retracted by spring 60. This movement willbring assm'se move only a short distance into contact with roller 53,and will move into fully retracted position when roller 53 has beenmoved below cam portion 65, approximately at the end of the actuatorcycle. As the actuators pass through the full cycle position, roller 53will rise and lever 54 will be rocked counterclockwise, bringing pawl 83against roller 64, and rotating the driven member of the clutchsufficiently to allow the clutch pawl 36 to drop from engagement withplate 5| into engagement with the ratchet teeth of the drive member 38of the clutch.

The same operations will follow a stopping signal from the numeralswheels, transmitted through the known lever 3| operated by said wheelsand engaging an arm of the secondary latch 56.

The lever 54 will be reengaged with the'primary latch 55 during thefinal action of'the" auxiliary clutch by engagement of the roller 64with an arm 86 of said'lever (Fig. 13). The auxiliary clutch beingreengaged, will drive notched disk 41, forcing the roller of arm 48 outof the notch and thereby releasing the main clutch by the contact of arm49 with the pins of clutch lever'l I I.

The overrun of the differential actuators and the return thereof to fullcycle position is governed by means of a pair of cams 61, 88 (Figures 6,9 and 12), fast with the driven element of the auxiliary clutch andengaging rollers of the rocker frame 54. Actually, as shown, the cam 81forms such driven member, the pawls 36, 3! and the roller 64 beingmounted upon said cam. Preferably, the initial movement imparted to thecalculator drive by cam 68 is faster than the running speed of themachine, so that there will be no frictional resistance to thedisengagement of the main clutch. The cams are so designed that movementof the differential actuators from full cycle to full overrun positionwill be harmonieally retarded, and thereafter the actuators will bereturned to their full cycle position by a harmonically accelerated andretarded movement. Toward the end of this operation the cams l5 effectthe final restoration and locking of the actuators in their full cycleposition.

As the cams come back into the positions illustrated in Figs. 5 and 6,the pawl 36 of the auxiliary clutch will contact the detent 35 and thepawls will be lifted out of engagement with the teeth of driving member39. At the same time a lug 69 of cam 61 will engage the end of detent 35as seen in Figure '7, arresting the movement of the driven members ofthe auxiliary clutch mechanism. I

I claim:

1. In a motor driven calculating machine having power transmissioncontrol me 5 including two members engageable to effect t etransmission, an operating shaft cyclically driven under control of saidmeans, and engaging means alternately adjustable to engage and todisengage said transmission control elements; an auxiliary clutch, poweroperated means acting to engage the auxiliary clutch, and means operableby the auxiliary clutch and cooperating with the engaging mean todisengage the transmission control elements and acting to drive theoperating shaft first through a given number of degrees of rotationbeyond and thereafter reversely back to full-cycle position.

.2. In a motor driven calculating machine having power transmissioncontrol means includins two members engageable to eilect thetransmission, an operating shaft cyclically driven under control of saidmeans, and engaging means alternately adjustable to engage and todisengage said transmission control elements; an auxiliary clutch, poweroperated means acting to engage the auxiliary clutch, and means operableby the auxiliary clutch and including elements acting to adjust theengaging means to disengage the tron control elements and cams rotatableto drive the operating shaft first through a given number of degrees ofrotation beyond its full-cycle position at a harmonically diminishingspeed and thereafter reversely back to said full-cycle position.

3. In a motor driven calculating machine having power transmissioncontrol means including two members engageable to effect thetransmission. an operating shaft cyclically driven alternatively in oneor in the other direction under control of said means, and provided witha crank arm, and engaging means alternately adjustable to engage and todisengage said transmission control-elements; an oscillatory arm, a linkconnecting said arm with the crank arm of the operating shaft andmaintaining the parts out of dead center position, an auxiliary clutch,and means operable by the auxiliary clutch and including elements actingto adjust the engaging means to disengage the transmission controlelements and cams rotatable to drive the oscillating arm. to eflectmovement of the operating shaft through a given number of degrees ofrotation beyond its full-cycle position.

4. In a motor driven calculating machine having power transmissioncontrol means including two members engageable to effect thetransmission, an operating shaft cyclically driven under control of saidmeans, and engaging means alternately adjustable to engage and todisengage said transmission control elements; an auxiliary one cycleclutch cooperating with the engaging means to engage the transmissioncontrol elements, means for disengaging the auxiliary clutch in midcycle position, power operated means acting to reengage the auxiliaryclutch, and cam means driven by the auxiliary clutch to operate andlocate the operating shaft, including elements normally holding saidshaft in full-cycle position, elements cooperating with the engagingmeans upon initial action of the auxiliary clutch to disengage thetransmission control elements, and elements operable upon reengagementof the auxiliary clutch to drive the operating shaft first beyond andthereafter reversely back to its full-cycle position, said cam meansbeing designed in the position assumed thereby in the mid-cycledisengaged position of the auxiliary clutch, to release the operatingshaft for rotation through the transmission control means.

5. In a motor driven'calculating machinehaving a power transmissioncontrol means includ- 1113 two members engageable to effect thetransmission, machine operating means cyclically driven under control ofsaid means, and engaging means alternately adjustable to engage and todisengage said transmission control elements; an auxiliary one cycleclutch cooperating with the engaging means to engage the transmissioncontrol elements, means for disengaging the auxiliary clutch inmid-cycle position, power operated means acting to reengage theauxiliary clutch, cam means driven by the auxiliary clutch during theinitial action thereof to condition the operating means for operation bysaid transmission control means, and cam means driven by the auxiliaryclutch during the final operation thereof to restore the operating meansto normal position of rest.

6. In a motor driven calculating machine having power transmissioncontrol means including two members engageable to effect thetransmission, machine operating means cyclically driven under control ofsaid means, engaging means alternately adjustable to engage and todisengage said transmission control elements, and means operable tosignal the completion of a machine operation; an auxiliary one cycleclutch cooperating with the engaging means to engage the transmissioncontrol elements, means for disengaging the auxiliary clutch inmid-cycle position, means operating in time with the machine operatingmeans and controlled by the signal means to reengage the auxiliaryclutch, cam means driven by the auxiliary clutch during the initialaction thereof to condition the operating means for operation by saidtransmission control means, and cam means driven by the auxiliary clutchduring the final operation thereof to restore the operating means tonormal position of rest.

7. In a motor driven calculating machine having an operating train; aclutch in said train comprising a toothed rotary driving member, arotary driven member, and a spring urged pawl mounted on said drivenmember, a stationary plate projecting into the path of movement of saidpawl and designed to disengage the pawl from the teeth of the drivingmember, and means for inparting sumcient rotary movement to the drivenmember to move the pawl out of contact with the plate and thereby allowengagement of the pawl with said teeth.

8. In a motor driven calculating machine having an operating train;control means interposed in said train and comprising a driventransmission member, rotary cam means for driving said member anddesigned in a given angular position to free said member for independentrelative movement, and a clutch comprising a toothed rotary drivingmember, a rotary driven member having driving connection with said cammeans, and a spring urged pawl mounted on said driven clutch member, astationary plate projecting into the path of movement of said pawl anddesigned to disengage the pawl from the teeth of the driving member asthe cam means move into position of independent movement relative to thedriven transmission member, and means for imparting sufficient rotarymovement to the driven clutch member to move the pawl out of contactwith the plate and thereby allow engagement of the pawl with said teeth.

9. In a motor driven calculating machine having an operating shaft, andpower transmission control-means including two members engageable toeffect the transmission selectively engageable to effect forward oralternatively reverse rotation of said shaft; engaging means including amember adjustable to determine engagement of the transmission controlelements for forward or alternatively for reverse rotation of the shaft,an auxiliary clutch, means operable by the auxiliary clutch to operatethe engaging means, an operation key, and means operable by said key toadjust the direction determining member of the engaging means and toengage the auxiliary clutch.

LORIN G PICKERING CROSMAN.

